WO1993021395A1 - Dispositif a circuit hydraulique destine aux machines de chantier - Google Patents

Dispositif a circuit hydraulique destine aux machines de chantier Download PDF

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Publication number
WO1993021395A1
WO1993021395A1 PCT/JP1993/000508 JP9300508W WO9321395A1 WO 1993021395 A1 WO1993021395 A1 WO 1993021395A1 JP 9300508 W JP9300508 W JP 9300508W WO 9321395 A1 WO9321395 A1 WO 9321395A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
traveling
signal
hydraulic
Prior art date
Application number
PCT/JP1993/000508
Other languages
English (en)
Japanese (ja)
Inventor
Genroku Sugiyama
Toichi Hirata
Original Assignee
Hitachi Construction Machinery Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Construction Machinery Co., Ltd. filed Critical Hitachi Construction Machinery Co., Ltd.
Priority to KR1019930703877A priority Critical patent/KR0132687B1/ko
Priority to EP93908117A priority patent/EP0593782B1/fr
Priority to DE69319400T priority patent/DE69319400T2/de
Priority to US08/142,366 priority patent/US5446979A/en
Publication of WO1993021395A1 publication Critical patent/WO1993021395A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2282—Systems using center bypass type changeover valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members

Definitions

  • the present invention relates to a hydraulic circuit device for civil engineering and construction equipment such as a hydraulic excavator, and in particular, in a construction machine in which left and right traveling motors drive left and right crawler tracks respectively, a combined operation of traveling and other working machines is possible.
  • hydraulic circuits for construction equipment such as hydraulic excavators.
  • a conventional hydraulic circuit device is composed of first and second hydraulic pumps and pressure oil discharged from the first and second hydraulic pumps.
  • a plurality of hydraulic actuators to be driven a first valve group connected to the discharge line of the first hydraulic pump, and controlling a flow rate of hydraulic oil supplied to the associated hydraulic actuator;
  • a second valve group that is connected to the discharge line of the second hydraulic pump and controls the flow rate of hydraulic oil supplied to the associated hydraulic factory.
  • the plurality of hydraulic actuators include, for example, first and second traveling motors that drive the left and right crawler tracks of the excavator, and a plurality of working equipment other than the first and second traveling motors, for example, the hydraulic excavator. It includes a turning motor for turning the arm, an arm cylinder for driving the arm, a boom cylinder for driving the boom, and a bucket cylinder for driving the bucket.
  • the first valve group includes a first traveling directional control valve for controlling a flow rate of the pressure oil supplied to the first traveling motor, and a plurality of work implement mechanisms.
  • the second valve group includes a plurality of second directional control valves for controlling the flow rate of the pressure oil supplied to at least a part of the plurality of work machines, for example, a second directional control valve for a boom, a bucket, A second directional control valve for the second traveling, a second directional switching valve for the second arm, and a second traveling directional switching valve for controlling the flow rate of the pressure oil supplied to the second traveling motor.
  • the directional control valve is connected in tandem so as to supply the hydraulic oil from the second hydraulic pump to the second travel motor with priority over the second directional control valve.
  • the hydraulic circuit device includes a hydraulic oil supply circuit for the second traveling directional control valve, which is connected to the first traveling motor other than the first and second traveling motors. It further has a communication circuit for communicating with the hydraulic oil supply circuit of the traveling ⁇ direction switching valve.
  • the communication circuit includes a branch passage that connects a discharge pipe line of the second hydraulic pump and an input port of the first traveling direction switching valve, and an on-off valve that is provided in the branch passage and opens and closes the branch passage.
  • a check valve provided downstream of the on-off valve to prevent backflow of hydraulic oil, wherein the first and second directional control valves related to the work equipment are not operated. Sometimes it is kept in the closed position and is switched to the open position when the first and second directional control valves operate.
  • This prior art focuses on improving the performance of a combined operation that simultaneously performs operations such as turning, boom, and arm in addition to traveling operation. For example, when the traveling alone operation is performed, since the on-off valve is kept at the closed position, the entire amount of the hydraulic oil of the first hydraulic pump is supplied to the first traveling motor via the first traveling direction switching valve. The entire amount of hydraulic oil in the second hydraulic pump is supplied to the second traveling mode via the second traveling direction switching valve, whereby the left and right crawler belts are driven and traveling is performed.
  • the load pressure of the first travel motor is higher than the load pressure of the second travel motor because the first and second travel direction switching valves are connected to the parallel in the combined operation of travel and work equipment.
  • the entire amount of the pressure oil of the second hydraulic pump flows into the first traveling motor, and accordingly, the operation of the second traveling motor may be incomplete.
  • the front truck eg, arm cylinder, boom cylinder
  • the first and second traction motors are operated, and the body is lifted so that the tip of the bucket contacts the ground surface.
  • the ground surface is slippery and When the frictional force between the belt and the ground contact surface is low, only the left crawler belt slips, the first traction motor spins, and the second traction motor stops operating. There is.
  • An object of the present invention is to provide a hydraulic circuit device for a civil engineering / construction machine that prevents a running failure caused by a difference in the magnitude of a load pressure between two traveling modes during a combined operation of a traveling machine and a working machine. Is to provide.
  • a first and second hydraulic pumps a plurality of hydraulic actuators driven by pressure oil discharged from the first and second hydraulic pumps; A first valve group connected to the discharge line of the hydraulic pump and controlling the flow rate of hydraulic oil supplied to the associated hydraulic factor; and connected to the discharge line of the second hydraulic pump, A second valve group for controlling the flow rate of hydraulic oil supplied to the hydraulic actuators; and the first and second traveling units each driving a pair of traveling devices.
  • a motor, and a plurality of working machines each driving a plurality of working machines, wherein the first valve group controls a flow rate of pressure oil supplied to the first traveling motor.
  • a traveling direction switching valve A plurality of first directional control valves for controlling a flow rate of the pressure oil supplied to at least a part of the industrial machine, and the plurality of first directional control valves for the first traveling.
  • the second valve group is connected to the second travel motor so as to supply the hydraulic oil from the first hydraulic pump to the associated work equipment overnight with priority over the direction switching valve.
  • a second traveling directional control valve for controlling a flow rate of the supplied pressure oil, and a plurality of second directions for controlling a flow rate of the pressure oil supplied to at least a part of the plurality of work machine functions.
  • the second travel direction switching valve has a higher priority than the plurality of second direction switching valves.
  • the first and second traveling direction switching valves are connected so as to supply pressure oil from a pump to the second traveling motor, and the first and second traveling direction switching valves are opened according to the operation amounts of the first and second operation means, respectively.
  • First and second variable throttles that change the area to control the flow rate of the pressure oil; and the second traveling direction switching in accordance with at least one operation of the plurality of working machines.
  • a hydraulic circuit device for a civil engineering / construction machine further comprising a communication circuit for communicating a pressure oil supply circuit of a valve with a pressure oil supply circuit of the first traveling direction switching valve, wherein (a) the first variable throttle and the First pressure adjusting means disposed between the first traveling motor and a downstream pressure of the first variable throttle to control the pressure to a value corresponding to the first signal pressure; and (b) the second variable throttle. And the second traveling motor, and the downstream pressure of the second variable throttle is reduced. And (c) a higher pressure of the load pressure of the first travel motor and the load pressure of the second travel motor. (D) at the time of a combined operation of simultaneously driving the first and second traveling motors and at least one of the plurality of working machines. Signal switching means for applying the maximum load pressure to the first and second pressure adjusting means as the first and second signal pressures.
  • a hydraulic circuit for a civil engineering / construction machine An apparatus is provided.
  • the pressure from the first hydraulic pump is controlled.
  • the oil is supplied to the corresponding work equipment through the first directional control valve of the first valve group, and the pressure oil supply circuit of the second directional control valve and the first directional control valve. Since the pressure oil supply circuit of the switching valve communicates through the communication circuit, the pressure oil from the second hydraulic pump communicates. It is supplied to both the first traveling motor and the second traveling motor via the road.
  • the signal switching means is operated in conjunction with the operation of the first and second traveling motors and the work machine, and the maximum load pressure detected by the pressure selecting means, that is, the first traveling motor
  • the pressure selecting means that is, the first traveling motor
  • This pressure is used to control the downstream pressure of the first variable throttle and the first pressure regulating means and the downstream of the second variable throttle. It is provided to each of the second pressure regulating means for controlling the pressure.
  • the downstream pressures of the first variable throttle and the second variable throttle are controlled to be equal to the above-mentioned maximum load pressure.
  • the upstream pressure of the first variable throttle and the second variable throttle is equal to the pressure of the hydraulic oil from the second hydraulic pump.
  • the differential pressure between the upstream pressure and the downstream pressure of the first variable throttle and the differential pressure between the upstream pressure and the downstream pressure of the second variable throttle are both equal, and the difference between the first travel motor and the second travel motor is equal.
  • each of the first traveling motor and the second traveling motor depends on the opening area of the first variable throttle and the second variable throttle. Supplied flow rate. Therefore, for example, even if the load pressure of the first traveling motor decreases, the pressure oil is also reliably supplied to the second traveling motor, and the operation of the second traveling motor does not stop. However, it is possible to prevent a situation in which the vehicle cannot travel.
  • the signal switching means is configured to be the maximum load pressure as the first and second signal pressures when at least one of the plurality of work machines is activated. Is applied to the first and second pressure adjusting means.
  • the signal switching means includes an operation detecting means for detecting at least one operation of the plurality of work machines, and the operation detecting means. 7
  • the load pressure of the associated actuator is applied as the first and second signal pressures to the first and second pressure adjusting means, respectively. It has at least one signal switching valve for applying the maximum load pressure to the first and second pressure adjusting means when the operation is detected.
  • the signal switching means sets the maximum load pressure as the first and second signal pressures to the first load pressure.
  • the second pressure adjusting means preferably, when the opening areas of the first and second variable diaphragms are equal to or smaller than a predetermined maximum opening area near the maximum, the signal switching means is used as the first and second signal pressures.
  • the load pressures of the relevant factories are applied to the first and second pressure adjusting means, respectively, the opening area of the first and second variable throttles becomes larger than the opening area near the maximum opening area.
  • at least one signal switching valve for applying the maximum load pressure as the first and second signal pressures to the first and second pressure adjusting means.
  • the first and second pressure adjusting means are pressure adjusting valves built in the first and second traveling direction switching valves, respectively.
  • the signal switching means has first and second signal switching valves provided for the first and second pressure adjusting means, respectively.
  • the signal switching means may include a single signal switching valve provided commonly to the first and second pressure adjusting means.
  • first and second pressure adjusting means are incorporated in the first and second traveling direction switching valves, respectively, and the signal switching means is provided in the first and second traveling direction switching valves.
  • the spool position It includes a switching passage that opens and closes first.
  • FIG. 1 is a circuit diagram showing a configuration of a hydraulic circuit device of a civil engineering / construction machine according to a first embodiment of the present invention.
  • FIG. 2 is a circuit diagram showing details of the first and second valve groups shown in FIG.
  • FIG. 3 is a side view of a hydraulic shovel on which the hydraulic circuit device shown in FIG. 1 is mounted.
  • FIG. 4 is a top view of the excavator.
  • FIG. 5 is a circuit diagram showing a configuration of an operation lever device for operating the directional control valves of the valve group shown in FIG. 1 and an operation detecting device for detecting the operation of the directional control valves.
  • FIG. 6 is a circuit diagram showing a configuration of a hydraulic circuit device according to a second embodiment of the present invention.
  • FIG. 7 is a circuit diagram showing a configuration of a hydraulic circuit device according to a third embodiment of the present invention.
  • FIG. 8 is a sectional view showing a structure of a main part of the traveling direction switching valve shown in FIG.
  • FIG. 9 is a circuit diagram showing a configuration of a hydraulic circuit device according to a fourth embodiment of the present invention.
  • FIG. 10 is a circuit diagram showing a configuration of a hydraulic circuit device according to a fifth embodiment of the present invention.
  • FIG. 11 is a circuit diagram showing a configuration of an operation lever device for operating the directional control valves of the valve group shown in FIG. 10 and an operation detecting device for detecting the operation of the directional control valves.
  • FIG. 12 shows a configuration of a hydraulic circuit device according to a sixth embodiment of the present invention.
  • FIG. 13 is a cross-sectional view showing a structure of a main part of the traveling direction switching valve shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIGS. 1 and 2 are circuit diagrams showing the configuration of a hydraulic circuit device of a hydraulic shovel cited as a first embodiment of the present invention.
  • first and second hydraulic pumps 35, 36 are swash plate pumps that adjust the pump discharge flow rate by changing the tilt angle (displacement volume) of the swash plate.
  • a well-known input torque limit regulator is provided, 150, 151. When the pump discharge pressure rises above a predetermined value, the swash plate tilt angle is reduced, and the pump discharge flow rate is reduced.
  • the input horsepower of 5, 36 is controlled not to exceed the output horsepower of the prime mover 37.
  • the input torque limit is set to 150, 151 in conjunction with the known torque control.
  • the discharge line 41 of the first hydraulic pump 35 is connected to the first valve group 39.
  • the first valve group 39 has a directional control valve 43 for turning at an upstream position, and thereafter, a directional control valve 44 for a first arm and a directional control valve 45 for a first boom are sequentially provided downstream thereof.
  • the first bucket directional switching valve 46 the left traveling directional valve which is the first traveling directional switching valve. It has a direction switching valve 47.
  • the turning directional control valve 43 is connected to a slewing motor 53 that drives the slewing body 200 of the hydraulic excavator shown in FIGS. 3 and 4, and the first arm directional switching valve 44 connects the arm 201.
  • the first boom direction switching valve 45 is connected to the driving arm cylinder 54, the first boom direction switching valve 45 is connected to the boom cylinder 55 driving the boom 202, and the first bucket direction switching valve 46 is connected to the arm cylinder 54.
  • the left traveling direction switching valve 47 is connected to a packet cylinder 56 that drives the left crawler belt 203, and the left traveling direction switching valve 47 is connected to a left traveling motor 57 that drives the left crawler belt 204.
  • the discharge line 42 of the second hydraulic pump 36 is connected to the second valve group 40.
  • the second valve group 40 has a right traveling directional switching valve 49 as a second traveling directional switching valve at an upstream position, and sequentially downstream of the second traveling direction switching valve 50, the second boom directional switching valve 50. And a second bucket directional switching valve 51 and a second arm directional switching valve 52.
  • the right traveling direction switching valve 49 is connected to a right traveling motor 58 for driving the right crawler belt 205 of the hydraulic excavator shown in FIGS. 3 and 4, and the second boom direction switching valve 50 is a boom 20.
  • the second packet directional switching valve 51 is connected to a bag cylinder 56 that drives a baggage 203, and is connected to a beam cylinder 55 that drives a baggage 203.
  • the direction switching valve 52 is connected to an arm cylinder 54 that drives the arm 201.
  • the revolving superstructure 200, boom 202, arm 201, and baguette 203 shown in FIGS. 3 and 4 described above constitute a hydraulic shovel working machine.
  • the arm 201 and the bucket 203 constitute a front mechanism of the hydraulic excavator, and the swing motor 53, the arm cylinder 54, the bump cylinder 55, and the bucket cylinder 56 described above work. It is a part of the machine act.
  • Turning directional control valve 43, 1st arm directional control valve 44, 1st boom directional control valve 45, the first bucket directional switching valve 46, the second boom directional switching valve 50, the second bucket ⁇ directional switching valve 51, and the second arm directional switching valve 52 The flow rate of pressurized oil supplied to these work machines is controlled.
  • the left traveling direction switching valve 47 is a left traveling motor.
  • the right flow direction switching valve 49 controls the flow rate of the pressure oil supplied to the right travel motor 58.
  • the directional control valve for turning 43, the first directional control valve for arm 44, the first directional control valve for boom 45, the first directional control valve for baguette 46 Supplies the hydraulic oil from the first hydraulic pump 35 to the associated work equipment 53, 54, 5.5, 56 with priority over the left-traveling directional control valve 47.
  • the right traveling direction switching valve 49 is a second boom ⁇ direction switching valve 50, a second bucket direction switching valve 51, and a second arm direction switching valve. It is connected to the evening dem to supply the pressure oil from the second hydraulic pump 36 to the right traveling motor 58 with priority over 52.
  • the turning direction switching valve 43 and the first arm direction switching valve 44 are connected in parallel to each other, and these direction switching valves 43, 44 and the first The boom directional control valve 45 and the first bucket directional control valve 46 are connected in tandem so that pressure oil is supplied preferentially in this order.
  • the second boom directional control valve 50 and the second bucket directional control valve 51 are connected in parallel to each other, and these directional control valves 50, 51 and the The directional switching valve 52 for the second arm is connected to the tandem so that the pressure oil is preferentially supplied in this order.
  • the discharge pipe line 42 of the second hydraulic pump 36 and the input port of the left traveling direction switching valve 47 are connected by a branch passage 59.
  • This branch The passage 59 has an on-off valve 60 for opening and closing the branch passage 59, and a check valve 6 provided downstream of the opening and closing valve 60 for preventing the backflow of the pressure oil in the direction of the discharge pipe 42. 1 is provided.
  • the on-off valve 60 is closed as shown in the figure when the directional control valves 43, 44, 45, 46 or the directional control valves 50, 51, 52 are not operating.
  • the directional control valve is maintained in a position, and is switched to the open position when at least one of these directional control valves is operated.
  • the above-mentioned branch passage 59, on-off valve 60 and check valve 61 are provided with work equipment other than the left traveling motor 57 and the right traveling motor 58 (rotating motor 53, arm cylinder 54, boom cylinder 5).
  • the hydraulic oil supply passages 1 and 3 for the left traveling direction switching valve 47 and the right oil direction switching valve 49 for at least one of the 5, 5, and 5 A communication circuit 110 is provided for communication with the communication circuit 4.
  • reference numeral 48 denotes a tank.
  • a power center balance valve 90 is provided between the left traveling direction switching valve 47 and the left traveling motor 57, and a counter is provided between the right traveling direction switching valve 49 and the right traveling motor 58.
  • Balance valve 91 is provided o
  • the directional control valves 43 to 47 and 49 to 52 are hydraulic pilot operated valves.
  • an operation lever device 1 shown in FIG. 60, 161, 162, 163, 164, 165, and 166 are provided as an operating means for operating these directional control valves to drive the corresponding actuators.
  • the operating lever device 16 1 is for turning, and generates pilot pressures A 1 and A 2 according to the operating direction and operating amount of the operating lever 16 1 a, and these pilot pressures A 1 and A 2 Is sent to the bit opening operation section of the turning direction switching valve 43.
  • the control lever device 1 6 2 is for the arm, and the piston according to the operation direction and the operation amount of the control lever 16 2 a
  • the pilot pressures Bl and B2 are generated and sent to the pilot operation sections of the directional control valves 44 and 52 for these pilot pressures Bl and B2.
  • the operating lever device 16 3 is for a boom, and generates pilot pressures CI and C 2 according to the operating direction and the operating amount of the operating lever 16 3 a.
  • C2 is sent to the pilot operation section of the boom directional control valves 45, 50.
  • the operation lever device 164 is for baguettes, and generates pilot pressures Dl and D2 according to the operation direction and the operation amount of the operation lever 1664a.
  • the on / off valve 60 is also a hydraulic pilot operation valve.
  • the operation signal pressures A, B, C, and D are detected by the operation detection device 170 shown in FIG. 0 is sent to the pilot operation section 60a, and the on-off valve 60 is switched from the closed position to the open position.
  • the operation detecting means 170 detects the pilot pressure A 1 or A 2 as the operation signal pressure A, and operates the shuttle valve 17 1 and the pilot pressure B 1 or B 2.
  • Shut-off valve 17 2 which detects as operation signal pressure B, pilot valve C 1 or 3 which detects pilot pressure C 1 or C 2 as operation signal pressure C, and pilot pressure D
  • Shuttle valve 1 7 4 for detecting 1 or D 2 as operation signal pressure D
  • shuttle valve 1 75 for detecting the higher of operation signal pressures A and B
  • Higher D And a shuttle valve 177 for detecting the higher of the operation signal pressure A or B and the operation signal pressure C or D.
  • the left traveling direction switching valve 47 changes the opening area in accordance with the operation amount of the operation lever 1 65 a to control the flow rate of the pressure oil supplied to the left traveling motor 57.
  • the right running direction switching valve 49 changes the opening area in accordance with the operation amount of the operating lever 166a to change the flow rate of the pressure oil supplied to the right running motor 58. It has second variable apertures 108 and 108a to be controlled. Other directional control valves have similar variable throttles.
  • An intermediate load passage 1 between the first variable throttle 107, 107a of the left traveling direction switching valve 47 and a pair of main pipelines 180, 181 of the left traveling motor 57. 0 5 is located, and the left directional switching valve 47 supplies pressure oil whose flow rate is controlled by the first variable throttles 107 and 107 a through the load passage 105 to the main pipeline 180. , 18 1 is switched and supplied.
  • An intermediate load passage is also provided between the first variable throttle 108, 108a of the right traveling directional valve 49 and a pair of main lines 18 2, 18 3 of the right traveling motor 58. 106 is located, and the right-way directional control valve 49 is connected to the main variable line 18 2 through the load passage 106 through the hydraulic oil whose flow rate is controlled by the second variable throttles 108 and 108 a. , And 183 are switched.
  • the first pressure regulator 130 is provided in the load passage 105 between the first variable throttle 107, 1a and the left traveling motor 57. Is arranged.
  • the first pressure regulator 130 controls the downstream pressure of the first variable restrictor 107, 107a to substantially match the first signal pressure provided via the signal line 132.
  • the second variable throttle 108, 108a is connected to the left traveling motor 58.
  • a second pressure regulator 133 is arranged in the load passage 106 between them. The second pressure regulator 133 controls the downstream pressure of the second variable throttles 108 and 108a so that it substantially matches the second signal pressure supplied through the signal line 134. I do.
  • the pressure generated in the load passage 105 of the left traveling direction switching valve 47 (load pressure of the left traveling motor 57) and the pressure generated in the load passage 106 of the right traveling direction switching valve 49 (A load pressure of the right traveling motor 58), a pressure selection means for detecting the higher pressure as the maximum load pressure, for example, a shuttle valve 13 6 and a first and second pressure regulator 1
  • First and second signal switching valves 13 1 and 13 5 that provide either the own load pressure or the maximum load pressure as the first and second signal pressures are installed at 30 and 13 33 respectively. Have been.
  • the first signal switching valve 13 1 does not operate any of the operation levers 16 1 a to 16 4 a, and when the on-off valve 60 is in the closed position shown in the drawing, the first signal switching valve 13 1 Outputs self-load pressure (load pressure of left traveling motor 57) as pressure, and when one of operation levers 16 1 a to l 64 a is operated and on-off valve 60 is switched to the open position That is, when at least one of the directional control valves 43, 44, 45, 46 or the directional control valves 50, 51, 52 relating to the work equipment is operated, the first signal is output.
  • the maximum load pressure selected by the shuttle valve 1366 is output as the pressure.
  • the second signal switching valve 1 35 also outputs its own load pressure (load pressure of the right traveling motor 58) as the second signal pressure.
  • load pressure of the right traveling motor 58 load pressure of the right traveling motor 58
  • the first and second signal switching valves 13 1 and 13 5 are each configured as a hydraulic pilot operation valve for the above purpose, and the operation shown in FIG. 5 is performed.
  • the springs 13 1 b and 13 35 b are used to maintain the operation signal pressures A, B, C and D are detected, and the operation signal pressure is sent to the pilot operation sections 13 1 a and 13 35 a, overcoming the forces of the springs 13 1 b and 135 b, and from the position shown in the figure. Is switched.
  • the operation levers 1665a and 1666a are operated for traveling forward only, and the left and right traveling direction switching valves 47 and 49 are respectively moved to the right positions in FIG. If it is switched, in this case, none of the operation levers 16 1 a to 16 4 a is operated, so none of the operation signal pressures A, B, C, and D is output, and the on-off valve 60 is in the closed position. Will be kept. Therefore, the entire amount of hydraulic oil of the first hydraulic pump 35 is supplied to the left traveling motor 57 via the left traveling direction switching valve 43, and the entire amount of hydraulic oil of the second hydraulic pump 36 is traveling right.
  • the load pressure of the left and right traveling motors 57, 58 is large. No, if In such a case, when the load pressure on the high pressure side (maximum load pressure) is given to the pressure regulator related to the low-pressure side traveling motor, the downstream pressure of the corresponding variable throttle is set to the maximum load pressure. As a result, the pressure difference across the pressure regulator becomes large and the pressure loss becomes remarkable. As a result, heat generation due to the pressure loss increases, and the life of hydraulic equipment is shortened due to the deterioration of heat balance.
  • the downstream pressure of each of the first variable throttles 107 and 107a and the second variable throttles 108 and 108a becomes its own load pressure. Since the pressure difference across the pressure regulators 130 and 133 is almost zero, there is almost no pressure loss of the pressure oil passing through the pressure regulators 130 and 133, and It is possible to suppress a decrease in the life of the hydraulic device due to deterioration of the balance.
  • the downstream pressure of the variable throttle associated with the low-pressure side traveling motor is controlled to be the maximum load pressure as described above, the discharge pressure of the corresponding hydraulic pump is also increased.
  • the discharge flow rates of the first and second hydraulic pumps 35 and 36 become high. Both may decrease and the traveling speed may decrease during steering operation.
  • the downstream pressure of the variable throttle associated with the low-pressure side traveling motor is maintained at the self-load pressure, the pump discharge pressure does not increase, and the discharge of the first and second hydraulic pumps 35, 36 is not performed. The flow does not decrease. Therefore, a decrease in the traveling speed during the steering operation is prevented, and high traveling performance can be secured.
  • the operation lever is intended to be a combined operation with turning 200, arm 201, boom 202, and baguette 203. Also operate one and the first valve
  • the first hydraulic pressure The pressure oil of the pump 35 is supplied to the corresponding directional control valve, the corresponding work equipment is driven, and one of the operation signal pressures A, B, C, and D is turned on and off by the on-off valve 60 and the first valve.
  • the on-off valve & 0 is switched from the closed position shown in FIG. 1 to the open position.
  • the shuttle valve 1 36 When the signal switching valves 13 1 and 13 5 are respectively switched from the positions shown in FIG. 1 due to the combined operation of the traveling and the working equipment described above, the shuttle valve 1 36 The maximum load that is the higher of the pressure generated in the load passage 105 of the left traveling motor 57 and the pressure generated in the load passage 106 of the right traveling motor 58, which was extracted in 6 The pressure is increased by the first pressure regulator 130 and the second pressure regulator 13 3 via each of these switching valves 13 1, 13 5 and the signal lines 13 2, 13 4. Given to. Thereby, the first pressure regulator 130 and the second pressure regulator 133 are provided with the corresponding first variable throttle 107 or 107 a and the second variable throttle 110 8.
  • the hydraulic oil from the second hydraulic pump 36 is located upstream of the first variable throttle 107 or 107a and the second variable throttle 108 or 108a, respectively.
  • the upstream pressures of these first variable throttles 107 or 107a and of the second variable throttles 108 or 108a are both equal. That is, the pressure difference between the upstream and downstream of the first variable throttle 107 or 107a and the second variable throttle 108 or 108a, that is, the differential pressure before and after the variable throttle, is Equal.
  • the front cylinder for example, the arm cylinder 54 and the boom cylinder 55 are driven together with the traveling motors 57 and 58, and the traveling is performed while the baguette contacts the ground surface.
  • the ground contact surface is slippery, and the frictional force between the left crawler belt 205 and the ground contact surface is small, so that the left crawler belt 205 is slippery and left Even in a situation where the load pressure on the traveling motor 57 is low and the vehicle is likely to run idle, the entire amount of the second hydraulic pump 36 flows to the left traveling direction switching valve 47 and the right traveling direction switching valve 49 To prevent the hydraulic oil from flowing to the left side. A flow rate according to the opening area is supplied, whereby straight traveling can be reliably realized.
  • another branch passage 1 that connects the discharge pipeline 41 of the first hydraulic pump 35 and the branch passage 59 located downstream of the check valve 61 is provided.
  • a flow control means for example, a fixed throttle 100 is provided in the other branch passage 102, and the fixed throttle 100, the branch passage 59 and another branch passage 10 are provided.
  • a check valve 101 for preventing backflow in the direction of the discharge pipeline 41 is provided between the connection point 2 and the connection point 2.
  • Other configurations are the same as those of the first embodiment.
  • the branch passage 102 and the fixed throttle 100 are not provided.
  • the hydraulic oil of the first hydraulic pump 35 is supplied to the working equipment at work, so it is located downstream of the work equipment at work.
  • the flow rate supplied to the left directional switching valve 47 is reduced as compared with the previous case, and there is a concern that the traveling speed may decrease and shock may occur.
  • the branch passage 100 and the fixed throttle 100 are provided so that when such traveling and the combined operation of the working machine are performed, part of the pressure oil of the first hydraulic pump 35 It flows to the left traveling direction switching valve 47 via the branch passage 102 and the fixed throttle 100 so that the traveling speed suddenly increases. It is possible to prevent the occurrence of lower and shog.
  • FIGS. 1 A third embodiment of the present invention will be described with reference to FIGS.
  • the same components as those shown in FIG. 1 are denoted by the same reference numerals.
  • the first pressure regulator 14 2, 14 2 a are incorporated in the left traveling direction switching valve 47 ⁇ , and are disposed corresponding to the left and right switching positions of the direction switching valve 47 A.
  • the second pressure regulators 1 4 3, 1 4 3 a are also incorporated in the right-hand directional switching valve 49 A, and correspond to the left and right switching positions of the directional switching valve 46 A, respectively. It is arranged.
  • Either the load pressure when the left traveling motor 57 is moving forward or the load pressure when moving backward is taken out and supplied to the pipeline connecting the shuttle valve 1336 and the first signal switching valve 131 Take out either the shuttle valve 140 or the load pressure of the right traveling motor 58 when moving forward or when moving backward, and connect the shuttle valve 1336 to the second signal switching valve 1335.
  • Other configurations are the same as those of the first embodiment shown in FIG. 1 described above.
  • FIG. 8 is a diagram showing a specific structure of a main part of a traveling direction switching valve provided in the third embodiment shown in FIG. In FIG. 8, for the sake of simplicity, only one side of the spool of each of the left-direction directional switching valve 47 A and the right-direction directional switching valve 49 A is shown.
  • the left traveling direction switching valve 47A is provided with a housing (land) 300 forming a port, a spool 301, and a slidably provided inside the spool 301. Composed of 1 pressure regulator 1 4 2 valve element 3 02, fixed to spool 3 0 1, and a spring 3 0 3 that regulates the stroke of valve element 3 02, and spring 3 4 I have.
  • the spool 301 is provided with various variable apertures (notches) including a first variable aperture 107.
  • FIG. 8 shows a neutral state in which the first variable throttle 107 provided on the spool 301 is closed. When the spool 301 is moved to the left in FIG.
  • the first signal pressure output from the first signal switching valve 13 1 is guided to the spring chamber 3 07 of the first pressure regulator 14 2 via the groove 308 and the passage 309. I will For this reason, the downstream pressure of the first variable throttle 107 is controlled to a pressure that takes into account the force of the spring 304 in addition to the first signal pressure. That is, if the force of the spring 304 is set to a very small value that can be ignored, when the own load pressure is guided to the spring chamber 307 as the first signal pressure, the first variable throttle 1
  • the downstream pressure of 07 was controlled so as to be maintained at its own load pressure, and the maximum load pressure selected by the shuttle valve 13 36 was guided to the spring chamber 3 07 as the first signal pressure. At this time, the downstream pressure of the first variable throttle 107 is controlled to be the maximum load pressure.
  • the right-way directional control valve 49 A is provided with a housing (land) 400 forming a port, a spool 401, and the spool 401.
  • the valve body 402 of the second pressure regulator 144 provided slidably in the inside of the 401 and the stopper 40 fixed to the spool 401 and defining the stroke of the valve body 402. 3 and a spring 4 0 4.
  • S The pool 401 has various variable apertures (notches) including a second variable aperture 108.
  • FIG. 7 shows a neutral state in which the second variable throttle 108 provided on the spool 401 is closed.
  • the pressure oil supplied from the pressure oil supply circuit 104 passes through the second variable throttle 108 to the passage 405.
  • the valve body 402 of the second pressure regulator 144 moves rightward against the force of the spring 404 by the pressure oil guided to the passage 405.
  • the pressure oil guided to 405 flows through the passage 406 to the load passage 106.
  • the second signal pressure output from the second signal switching valve 135 is guided to the spring chamber 407 of the second pressure regulator 144 via the groove 408 and the passage 409. I will Therefore, the downstream pressure of the second variable throttle 108 is controlled to a pressure that takes into account the force of the spring 404 in addition to the second signal pressure.
  • the second variable The downstream pressure of the throttle 108 is controlled so as to be maintained at its own load pressure, and the maximum load pressure selected by the shuttle valve 136 as the second signal pressure is the spring chamber 407
  • the downstream pressure of the second variable throttle 108 is controlled to be the maximum load pressure.
  • the first and second signal switching valves 13 1 and 13 5 are shown in FIG.
  • the maximum load pressure is guided to both the spring chambers 307 and 407, and the pressure difference between the front and rear of the first variable throttle 107 of the left directional switching valve 47A,
  • the pressure difference between the front and rear of the second variable throttle 108 of the directional control valve 49A for the right running becomes equal to the pressure difference between the front and rear. And straight running can be reliably realized.
  • FIG. 7 A fourth embodiment of the present invention will be described with reference to FIG. In the figure, the same components as those shown in FIG. 7 are denoted by the same reference numerals.
  • the fourth embodiment shown in FIG. 9 is connected to a shuttle valve 13 6 instead of the two signal switching valves 13 1, 13 5 in the third embodiment shown in FIG.
  • a single signal switching valve 155 is provided, and the higher of the pressure output from the signal switching valve 155 and the pressure extracted from the shuttle valve 140 is taken out and supplied to the signal path 132 The higher of the pressure output from the shuttle valve 150, the pressure output from the signal switching valve 1505, and the pressure output from the shuttle valve 140a is taken out and supplied to the signal passage 134.
  • a shuttle valve 150a is provided.
  • the signal switching valve 155 is a hydraulic pilot operation valve, and is located at the position shown when none of the operation signal pressures A, B, C, and D is applied.
  • the left traveling direction switching valve 47A and the right traveling direction switching valve 49A are switched to the right position in FIG. Since 55 is kept at the position shown in the figure, it is supplied to the shuttle valves 150 and 150a.
  • the output pressure of the supplied signal switching valve 155 is the tank pressure.
  • the load pressure of the left traveling motor 57 is supplied to the first pressure regulator 1442 through the shuttle valve 140, the shuttle valve 150, and the signal path 132, and
  • the downstream pressure of the variable throttle 107 is controlled to be the load pressure of the left traveling motor 57. Therefore, the differential pressure across the first variable throttle 107 is the difference between the pressure of the hydraulic oil from the first hydraulic pump 35 and the load pressure of the left traveling motor 57.
  • the load pressure of the right traveling motor 58 is supplied to the second pressure regulator 144 via the shuttle valve 140a, the shuttle valve 150a, and the signal passage 134.
  • the downstream pressure of the second variable throttle 108 is controlled to be the load pressure of the right traveling motor 58. Therefore, the differential pressure across the second variable throttle 108 is the difference between the pressure of the hydraulic oil from the second hydraulic pump 36 and the load pressure of the right traveling motor 58. In this manner, each of the traveling motors 57 and 58 can be driven without being affected by the load pressure of the other traveling motor. The same applies to the case where the vehicle retreats alone.
  • the signal switching valve 155 is switched from the position shown in the figure with the operation of the work machine operation, and the load pressure of the left traveling motor 57 is reduced to the shuttle valve 140.
  • the load pressure of the right traveling motor 58 is taken out of the shuttle valve 140a and supplied to the shuttle valve 1336, and is supplied to the shuttle valve 1336.
  • the higher of the load pressure of the left travel motor 57 and the load pressure of the right travel motor 58 is taken out as the maximum load pressure, and the signal switching valve 155, the shuttle valve 155,
  • the signal is supplied to the first pressure regulator 14 2 via the signal passage 13 2, and at the same time, for example, via the signal passage 13 4 4 1st variable throttle 1 0 7 given to pressure regulator 1 4 3
  • the downstream pressure of the second variable throttle 108 is controlled so as to be the maximum load pressure.
  • the hydraulic oil of the second hydraulic pump 36 is supplied to both the left traveling direction switching valve 47A and the right traveling direction switching valve 49A.
  • the differential pressure across the first variable throttle 107 and the second variable throttle 1 and 8 is the difference between the pressure of the hydraulic oil from the second hydraulic pump 36 and the maximum load pressure. . Therefore, even in the fourth embodiment, each of the traveling directional control valves 47 A and 49 A is mutually independent of the magnitude of the load pressure between the traveling motors 57 and 58.
  • the flow rate according to the opening area can be supplied to the left and right traveling motors 57 and 58, and the straight traveling can be reliably realized in the combined operation of the traveling and the working machine as in the first embodiment described above.
  • FIGS. 1, 5 and 6 A fifth embodiment of the present invention will be described with reference to FIGS.
  • the same components as those shown in FIGS. 1, 5 and 6 described above are denoted by the same reference numerals.
  • the discharge pipeline 41 of the first hydraulic pump 35 and the portion of the first branch passage 59 located downstream of the check valve 61 correspond to the second embodiment shown in FIG. In the same manner as in the above, they are connected by a second branch passage 102 provided with a fixed throttle 1 check valve 101.
  • the first and second signal regulators 13 1 B and 13 3 are supplied to the first and second pressure regulators 13 0 and 13 33 in the same manner as in the first embodiment shown in FIG. 5 B is provided.
  • the first signal switching valve 13 1 B is configured such that the opening areas of the first variable throttles 10 7 and 10 7 a included in the left traveling ⁇ direction switching valve 47 are close to the maximum.
  • the self-load pressure (load pressure of the left traveling motor 57) is output as the first signal pressure in the range of the predetermined opening area or less, and the opening area of the first variable throttle 1st, 107a is close to the maximum.
  • the first signal pressure It is configured to output the maximum load pressure selected by the shuttle valve 13 6.
  • the opening area of the second variable throttles 108, 108 a included in the right traveling direction switching valve 49 is smaller than the predetermined opening area near the maximum.
  • the self-load pressure (load pressure of the right traveling motor 58) is output as the second signal pressure
  • the opening area of the second variable throttles 108, 108a is a predetermined opening area near the maximum.
  • the maximum load pressure selected by the shuttle valve 1336 is output as the second signal pressure.
  • the operation lever devices 165 and 166 shown in FIG. 11 have a shuttle valve 1 which detects the pilot pressure X 1 or X 2 as the operation signal pressure X as the operation detection means. 8 and pilot pressures Y1 or Y2 are provided as operation signal pressures Y. Shuttle valves 1-9 are provided. When these operation signal pressures X and Y are detected, the operation signal pressures are reduced. The first and second signal switching valves 1311B and 1335B are sent to the pilot operation sections 1331a and 135a, respectively.
  • the spring 13 1 b B of the first signal switching valve 13 1 B is provided with a first variable throttle 10 7 in which the pilot pressures XI and X 2 are included in the left traveling direction switching valve 47.
  • the first signal switching valve 13 1 is shown by overcoming the urging force of the operating signal pressure X at that time.
  • the pilot pressures XI and X2 reach the level that makes the opening area of the first variable throttles 107 and 107a larger than the predetermined opening area, the operation signal at that time is held.
  • the urging force by the pressure X is set to a level that switches the first signal switching valve 13 1 from the position shown in the figure.
  • the first variable throttle 10 0 in which the pilot pressures Y 1 and Y 2 are included in the right-direction switching valve 49 The opening area of 8, 108 a is set to be equal to or less than the predetermined opening area near the maximum.
  • the second signal switching valve 135 is maintained at the position shown in the figure by overcoming the urging force of the operating signal pressure Y at that time, and the pilot pressure Yl, ⁇ 2 is changed by the first variable.
  • the opening area of the apertures 108 and 108a becomes larger than the predetermined opening area, the urging force by the operating signal pressure Y at that time causes the second signal switching valve 135 to move from the position shown in the figure.
  • the switching strength is set.
  • the operation levers 165a and 166a are operated for the sole driving operation, and the left and right traveling direction switching valves 47 and 49 are respectively switched to, for example, the right position in FIG.
  • none of the operation levers 16 1 a to 16 4 a is operated, so that the operation signal pressures A, B, C, and D are not output, and the open / close valve 60 is in the closed position. Is kept. Therefore, the entire amount of the hydraulic oil of the first hydraulic pump 35 is supplied to the left traveling motor 57 through the left traveling direction switching valve 43, and the entire amount of the hydraulic oil of the second hydraulic pump 36 is traveling right.
  • the downstream pressure of the first variable throttle 1 and 7, 107a is the load pressure of the left traveling motor 57, that is, its own load pressure.
  • the downstream pressure of the variable throttles 108, 108a is the load pressure of the right traveling motor 58, that is, its own load pressure, and the traveling motors 51, 58 are connected to each other by the load pressure of the other traveling motor. N running that can be driven without being affected The same applies to the case of row retreat alone.
  • the pilot G when operating the operating levers 16a and 16a to, for example, a full stroke in order to realize traveling, the pilot G
  • the pressures X 1 or X 2 and Y 1 or Y 2 are the opening areas of the first and second variable apertures 107, 107 a and 108, 108 a, respectively.
  • the level becomes larger, and the first and second signal switching valves 131, 135 are switched from the position shown in FIG.
  • the operating lever -165, 166a is operated to a full stroke or a stroke similar thereto, and the first and second variable throttles 10
  • the opening areas of 7, 7a and 108, 108a are larger than the predetermined opening area near the maximum.
  • the load passage 105 of the left traveling motor 57 taken out by the shuttle valve 13 36 is transferred to the load passage 105.
  • the maximum load pressure which is the higher of the generated pressure and the pressure generated in the load passage 106 of the right travel motor 58, is the switching valve 1 3 1, 1 3 5 and the signal passage 13
  • the first pressure regulator 130 and the second pressure regulator 133 are supplied to the first pressure regulator 130 and the second pressure regulator 133 via the second and the second 134, respectively.
  • the first pressure regulator 130 and the second pressure regulator 133 are provided with the corresponding first variable restrictor 107 or 107a, and the second variable restrictor 108 or Control is performed so that the downstream pressure of 108 a becomes the maximum load pressure.
  • the pressure oil of the second hydraulic pump 36 is given to the first variable throttle 107 or 110a and the second variable throttle 108 or 108a, these first variable throttle 1 0 7 or 1 0 7 a, ⁇ beauty upstream pressure of the second variable throttle 1 0 8 or 1 0 8 a are both equal to c That is, the pressure difference between the upstream and downstream of the first variable throttle 107 or 107a and the second variable throttle 108 or 108a, that is, the differential pressure across the variable throttle is Both are equal.
  • the opening areas of the traveling direction switching valves 47 and 49 are mutually independent of each other regardless of the difference in the magnitude of the load pressure between the traveling motors 57 and 58.
  • a flow rate according to the above can be supplied to the left and right traveling motors 57, 58, and the straight traveling can be reliably realized at the time of the combined operation of the traveling and the working machine as in the first embodiment described above.
  • the first and second signal switching valves 1311 and 1335 are not shown in FIG. It is switched from the position shown in Fig. 10 so that the downstream pressure of the first variable restrictor 107 or 107a and the second variable restrictor 108 or 108a becomes the maximum load pressure. Controlled.
  • the differential pressures before and after the first and second variable throttles are substantially the same, and straight traveling can be reliably realized as in the case of the combined operation of the traveling and the working machine.
  • the left traveling direction switching valve 47 C is connected to the first pressure regulators 142, 142 a by switching the left traveling direction switching valve 47 C left and right.
  • the right-hand directional control valve 49 C is also provided with a second pressure regulator 14 3, 14 3 a for the right-hand directional control valve 49 C.
  • the opening area of the first and second variable apertures 107 or 107a and 108 or 108a is the smallest. When the opening area is larger than the predetermined opening area in the vicinity of the large, the maximum load pressure is used as the first and second signal pressures by the first and second pressure regulators 14 2, 14 2 a and 14 3, 14.
  • the signal switching means provided to 3a is constituted by switching passages 141, 141a on spools provided in the traveling direction switching valves 47C, 49C.
  • each of the traveling direction switching valves 47 C and 49 C is configured to have an intermediate position and a maximum operation position in the left and right switching directions in addition to the neutral position.
  • Other configurations are the same as those of the above-described fourth embodiment.
  • FIG. 13 is a diagram showing a specific structure of a main part of a traveling direction switching valve provided in the sixth embodiment shown in FIG. For simplicity, FIG. 13 shows only one side of the spool of each of the left traveling direction switching valve 47C and the right traveling direction switching valve 49C.
  • the directional control valve 47 C for left traveling includes a housing (land) 300 forming a port, a spool 301, and a first pressure slidably provided in the spool 301.
  • FIG. 13 shows a neutral state in which the first variable throttle 107 provided on the spool 301 is closed.
  • the pressure oil supplied from the pressure oil supply circuit 103 passes through the first variable throttle 107 and the passages 3 and 5 to the left. It is led to the load passage 1, which is connected to the traveling motor 57.
  • the valve element 302 of the first pressure regulator 1442 uses the spring 3 At the force of 04, it moves to the right, and the pressure oil guided to passage 305 flows out through load passage 305 through passage 306.
  • the pressure in the load passage 105 is guided to the spring chamber 307 of the first pressure regulator 144 through the groove 310, the passage 311 and the small hole 313.
  • the downstream pressure of the first variable throttle 107 is controlled to the pressure in the load passage 105 and the pressure in consideration of the spring force. That is, if the force of the spring 304 is set to a small value that can be ignored, the downstream pressure of the first variable throttle 107 is controlled so as to be maintained at the load pressure.
  • the right-running directional control valve 49 C is slidable in a housing (land) 400 forming a port, a spool 401, and the spool 401.
  • a second pressure regulator 14 3 provided at the valve 40 2, a stopper 40 3 fixed to the spool 401 and defining a stroke of the valve 402, and a spring. 4 0 4
  • the spool 401 has various variable apertures (notches) including a second variable aperture 108.
  • FIG. 13 shows a neutral state in which the second variable throttle 108 provided on the spool 401 is closed. When the spool 401 is moved to the left in FIG.
  • the pressure oil supplied from the pressure oil supply circuit 104 passes through the second variable throttle 108 and the passage 405 to the right. It is guided to a load passage 106 connected to the traveling motor 58.
  • the valve element 402 of the second pressure regulator 144 is pushed by the pressure oil guided to the passage 405 to the force of the spring 404.
  • the pressure oil guided to the passage 405 flows into the load passage 106 through the passage 406, and at this time, the spring chamber 407 of the second pressure regulator 144 is formed.
  • the pressure of the load passage 106 is conducted through the groove 411, the passage 411, and the small hole 413.
  • the pressure downstream of the second variable throttle 108 is The pressure is controlled to the pressure of the road 106 and the pressure taking into account the spring force. In other words, if the force of the spring 404 is set to a small value that can be ignored, the downstream pressure of the second variable throttle 108 is controlled so as to be maintained at the load pressure.
  • Control is performed so that the pressure of 305 and 405 becomes the pressure of the load passages 105 and 106.
  • the maximum load pressure taken out by the shuttle valve 1336 passes through the pipeline 190. It is led to the switching passage 141 formed by the groove 308C and the passage 309, and to the switching passage 141a formed by the groove 408C and the passage 409. In this case, on the left traveling directional switching valve 47 C side, since the passage 309 opens to the groove 308 C and at the same time the groove 310 and the passage 321 close, the first pressure The pressure in the spring chamber 307 of the force adjuster 142 becomes the maximum load pressure described above.
  • the differential pressure across the first variable throttle 107 on the C side is equal to the differential pressure across the right variable direction switching valve 49 9 C-side second variable throttle 108, As described above, it is possible to supply the same amount of pressurized oil according to the maximum opening area to both the left traveling motor 57 and the right traveling motor 58, so that straight traveling can be reliably realized.
  • the present invention is configured as described above, at the time of combined operation of traveling and a working machine, it is possible to prevent traveling impossibility caused by a difference in the load pressure between the two traveling motors, thereby preventing straight traveling. As a result, it is possible to achieve superior running operability when combined with running and work equipment compared to the past.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

On décrit un dispositif à circuit hydraulique destiné aux machines de chantier où un premier régulateur de pression (130), destiné à contrôler la pression aval grâce à des premiers dispositifs de restriction variable (107, 107a) pour la faire correspondre à un premier signal de pression, est disposé entre les premiers dispositifs de restriction variable d'une valve de contrôle directionnelle (47) permettant un déplacement vers la gauche et un premier moteur (57), alors qu'un deuxième régulateur de pression (133), destiné à contrôler la pression aval grâce à des deuxièmes dispositifs de restriction variable (108, 108a) pour la faire correspondre à un deuxième signal de pression, est disposé entre les deuxièmes dispositifs de restriction variable d'une valve de contrôle directionnelle (49) permettant un déplacement vers la droite et un deuxième moteur (57). Une valve à alternance (136) détecte une pression négative, la plus élevée de celles engendrées par ce premier ou ce deuxième moteur, qui devient la pression négative maximum, et des valves à commutation de signal (131, 135, 170) interviennent pendant un fonctionnement combiné où les deux moteurs et l'un au moins des divers actuateurs de machine fonctionnelle (53 à 56) sont entraînés simultanément, la pression négative maximum étant alors communiquée aux deux régulateurs de pression grâce à deux signaux de pression. Même quand on peut ainsi mettre en fonction un circuit de communication (110) alors que les actuateurs de machine agissent pendant un fonctionnement et son déplacement, ce qui permet à un circuit d'alimentation en huile de pression (104) commandé par la deuxième valve de contrôle directionnelle permettant le déplacement vers la droite et à un circuit d'alimentation en huile de pression (103) commandé par la première valve de contrôle directionnelle permettant le déplacement vers la gauche, de communiquer, les différences de pression traversant les deux dispositifs de restriction qui s'annulent en pratique et rendent ainsi possible un déplacement en ligne droite.
PCT/JP1993/000508 1992-04-20 1993-04-20 Dispositif a circuit hydraulique destine aux machines de chantier WO1993021395A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
KR1019930703877A KR0132687B1 (ko) 1992-04-20 1993-04-20 토목, 건설기계의 유압회로장치
EP93908117A EP0593782B1 (fr) 1992-04-20 1993-04-20 Dispositif a circuit hydraulique destine aux machines de chantier
DE69319400T DE69319400T2 (de) 1992-04-20 1993-04-20 Hydraulische schaltungsanordnung für erdbewegungsmaschinen
US08/142,366 US5446979A (en) 1992-04-20 1993-04-20 Hydraulic circuit system for civil engineering and construction machines

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP9980192 1992-04-20
JP9980292 1992-04-20
JP4/99802 1992-04-20
JP4/99801 1992-04-20

Publications (1)

Publication Number Publication Date
WO1993021395A1 true WO1993021395A1 (fr) 1993-10-28

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PCT/JP1993/000508 WO1993021395A1 (fr) 1992-04-20 1993-04-20 Dispositif a circuit hydraulique destine aux machines de chantier

Country Status (5)

Country Link
US (1) US5446979A (fr)
EP (1) EP0593782B1 (fr)
KR (1) KR0132687B1 (fr)
DE (1) DE69319400T2 (fr)
WO (1) WO1993021395A1 (fr)

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EP0593782A1 (fr) 1994-04-27
KR940701487A (ko) 1994-05-28
EP0593782B1 (fr) 1998-07-01
KR0132687B1 (ko) 1998-04-18
DE69319400D1 (de) 1998-08-06
US5446979A (en) 1995-09-05
DE69319400T2 (de) 1998-12-03
EP0593782A4 (fr) 1995-03-22

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